Technical Field
[0001] The present invention relates a vehicle driving system which includes an internal
combustion engine and an electric motor.
Background Art
[0002] Conventionally, with a view to preventing a shock that will result from a torque
interruption occurring during a gear change based on a transmission in which gear
change operations of a manual transmission with a high transmission efficiency are
automated, there have been proposed vehicle driving systems for hybrid vehicles which
include a twin-clutch type transmission in which two input shafts each have a gear
group and can individually be connected to an engine via a corresponding clutch, and
one of the input shafts can be driven by a motor generator (refer to Patent Literature
1).
[0003] In a vehicle driving system 200 of Patent Literature 1, as shown in Fig. 19, two
input shafts 201, 202 are connected individually to an engine Eng via clutches Cl,
C2, and further, a motor generator MG is connected to the input shaft 202. In addition,
by engaging a dog clutch 205, the input shaft 202 is connected to a countershaft 207
via a low-speed side gear train 206, and the input shaft 201 is connected to the countershaft
207 via a high-speed side gear train 209 by engaging a dog clutch 208.
[0004] It is disclosed that the motor generator MG is driven by a driving force from the
countershaft 207 so as to generate electricity through regeneration, and when the
clutch C2 is engaged, the motor generator MG is driven by the engine Eng to thereby
generate electricity.
Related Art Literature
Patent Literature
Summary of the Invention
Problem that the Invention is to Solve
[0006] In the vehicle driving system 200, however, nothing is described as to how to generate
a braking force while the vehicle is driven on the motor. In general, in the hybrid
vehicle, it is an important issue to generate electricity by the motor with good efficiency
by making use of the braking force of the vehicle.
[0007] The invention has been made in view of these situations and an object thereof is
to provide a vehicle driving system which can generate electricity by making use of
the braking force while the vehicle is running on the motor.
Means for Solving the Problem
[0008] Claim 1 provides a vehicle driving system (e.g., vehicle driving systems 1, 1A in
embodiment) comprising an internal combustion engine (e.g., engines 6 in embodiment)
and an electric motor (e.g., motors 7 in embodiment), the system comprising:
an internal combustion engine output shaft (e.g., crankshafts 6a in embodiment) by
which power is outputted from the internal combustion engine;
a first input shaft (e.g., first output shafts 11 in embodiment) which is disposed
parallel to the internal combustion engine output shaft and which is selectively connected
to the internal combustion engine output shaft by a first engaging and disengaging
unit (e.g., first clutches 41 in embodiment);
a second input shaft (e.g., second intermediate shafts 16 in embodiment) which is
disposed parallel to the internal combustion engine output shaft and which is selectively
connected to the internal combustion engine output shaft by a second engaging and
disengaging unit (e.g., a second clutch 42 in embodiment);
an output/input shaft (e.g., countershafts 14 in embodiment) which is disposed parallel
to the internal combustion engine output shaft and which outputs power to a driven
portion (e.g., drive wheels DW, DW in embodiment);
a first gear group which is disposed on the first input shaft and which includes a
plurality of gears (e.g., third speed drive gears 22a, fifth speed drive gears 25a,
a seventh speed drive gear 97a in embodiment) which are selectively connected to the
first input shaft via a first changeover unit (e.g., first change-speed shifters 51,
51A, a third change-speed shifter 52B, locking mechanisms 61 in embodiment);
a second gear group which is disposed on the second input shaft and which includes
a plurality of gears (e.g., second speed drive gears 22a, fourth speed drive gears
24a, a sixth speed drive gear 96a in embodiment) which are selectively connected to
the second input shaft via a second changeover unit (e.g., second change-speed shifters
52, 52A, a fourth change-speed shifter 52B in embodiment); and
a third gear group which is disposed on the output/input shaft and which includes
a plurality of gears (e.g., first common driven gears 23b, second common driven gears
24b, a third common driven gear 96 in embodiment) with which the gears of the first
gear group and the gears of the second gear group mesh,
wherein, when the vehicle is decelerated during an EV running by selecting a high-speed
side gear of the first gear group, a braking force during a downshift is ensured by
actuating wheel brakes in a cooperative fashion so as to compensate for a reduction
in regenerative braking force of the electric motor during a downward gear change
from the high-speed side gear to a low-speed side gear while regeneration is brought
about by the electric motor.
[0009] Claim 2 provides, based on Claim l, the system,
wherein the first changeover unit is a synchro clutch.
[0010] Claim 3 provides, based on Claim 1 or 2, the system,
wherein, when a vehicle speed is decreased to a predetermined value by bringing about
a regeneration by selecting the low-speed side gear, the regeneration is stopped,
and a low-speed side gear which is lower than the low-speed side gear is selected.
[0011] Claim 4 provides, based on any of Claims 1 to 3, the system,
wherein a regeneration amount can be increased in accordance with a pedal effort applied
to a brake pedal (e.g., brake pedals 111 in embodiment), and a braking force is ensured
by controlling a hydraulic pressure of a master cylinder (e.g., master cylinders M
in embodiment) for the first time after the regeneration amount reaches a regeneration
limit.
[0012] Claim 5 provides a vehicle driving system (e.g., vehicle driving systems 1, 1A in
embodiment) comprising an internal combustion engine (e.g., engines 6 in embodiment)
and an electric motor (e.g., motors 7 in embodiment), the system comprising:
an internal combustion engine output shaft (e.g., crankshafts 6a in embodiment) by
which power is outputted from the internal combustion engine;
a first input shaft (e.g., first output shafts 11 in embodiment) which is disposed
parallel to the internal combustion engine output shaft and which is selectively connected
to the internal combustion engine output shaft by a first engaging and disengaging
unit (e.g., first clutches 41 in embodiment);
a second input shaft (e.g., second intermediate shafts 16 in embodiment) which is
disposed parallel to the internal combustion engine output shaft and which is selectively
connected to the internal combustion engine output shaft by a second engaging and
disengaging unit (e.g., a second clutch 42 in embodiment);
an output/input shaft (e.g., countershafts 14 in embodiment) which is disposed parallel
to the internal combustion engine output shaft and which outputs power to a driven
portion (e.g., drive wheels DW, DW in embodiment);
a first gear group which is disposed on the first input shaft and which includes a
plurality of gears (e.g., third speed drive gears 22a, fifth speed drive gears 25a,
a seventh speed drive gear 97a in embodiment) which are selectively connected to the
first input shaft via a first changeover unit (e.g., first change-speed shifters 51,
51A, a third change-speed shifter 52B, locking mechanisms 61 in embodiment);
a second gear group which is disposed on the second input shaft and which includes
a plurality of gears (e.g., second speed drive gears 22a, fourth speed drive gears
24a, a sixth speed drive gear 96a in embodiment) which are selectively connected to
the second input shaft via a second changeover unit (e.g., second change-speed shifters
52, 52A, a fourth change-speed shifter 52B in embodiment); and
a third gear group which is disposed on the output/input shaft and which includes
a plurality of gears (e.g., first common driven gears 23b, second common driven gears
24b, a third common driven gear 96 in embodiment) with which the gears of the first
gear group and the gears of the second gear group mesh,
wherein, when the vehicle is decelerated during an EV running by selecting a high-speed
side gear of the first gear group, a braking force during a downshift is ensured by
making use of engine braking effects by engaging the second engaging and disengaging
unit in such a state that the internal combustion engine is started and one of the
gears of the second gear group is selected by the second changeover unit during a
downward gear change from the high-speed side gear to a low-speed side gear while
regeneration is brought about by the electric motor.
[0013] Claim 6 provides, based on Claim 5, the system,
wherein the system estimates a deceleration request, and
wherein, when a deceleration request to the low-speed side gear of the first gear
group is made while the regeneration is being brought about by the high-speed side
gear of the first gear group, engine braking is once attained in such a state that
the gear of the second gear group is selected, and a pre-downshift from the high-speed
gear to the low-speed side gear of the first gear group is made while the vehicle
is running on the gear of the second gear group.
[0014] Claim 7 provides, based on Claim 5 or 6, the system,
wherein the first changeover unit is a synchro clutch.
[0015] Claim 8 provides, based on any of Claims 5 to 7, the system,
wherein, when a vehicle speed is decreased to a predetermined value (e.g., a vehicle
speed Vf in embodiment) by bringing about a regeneration by selecting the low-speed
side gear, the regeneration is stopped, and a low-speed side gear which is lower than
the low-speed side gear is selected.
Advantage of the Invention
[0016] According to Claim 1, when decelerating the vehicle during the EV running, by ensuring
the braking force by actuating the wheel brakes in cooperation with the regenerative
braking by the electric motor, energy discharged from the wheel brakes as thermal
energy can be made effective use of as regenerative energy. In addition, the vehicle
is decelerated in accordance with the vehicle speed, and therefore, when the vehicle
is reaccelerated, the vehicle can be accelerated in a smooth fashion.
[0017] According to Claim 2, the gear change can be performed smoothly.
Additionally, the loss of regenerative torque (braking force) as a result of the use
of the synchro clutch is compensated for by engine braking, which can be made effective
use of as regenerative energy.
[0018] According to Claim 3, when the vehicle speed is decreased to a regeneration impossible
speed by the regeneration of the electric motor, the low-speed side gear which is
lower than the low-speed side gear is selected to put the vehicle ready for reacceleration
or start from standstill, thereby making it possible to smoothly accelerate or start
the vehicle from standstill.
[0019] According to Claim 4, the vehicle can be slowed down by making full use of the regeneration
of the electric motor.
[0020] According to Claim 5, when decelerating the vehicle during the EV running, by compensating
for the loss of braking force during downshifting by engine braking effects, energy
discharged by the mechanical brakes as thermal energy can be made effective use of
as regenerative energy. In addition, the vehicle is decelerated in accordance with
the vehicle speed, when reaccelerating the vehicle, the vehicle can be accelerated
in a smooth fashion.
[0021] According to Claim 6, when decelerating the vehicle during the EV running, the utilization
efficiency of energy can be increased by performing downshifting while making use
of engine braking effects.
[0022] According to Claim 7, the gear change can be performed smoothly.
In addition, the loss of regenerative torque (braking force) as a result of the use
of the synchro clutch is compensated for by the engine braking, which can be made
effective use of as regenerative energy.
[0023] According to Claim 8, when the vehicle speed is decreased to a regeneration impossible
speed by the regeneration of the electric motor, the low-speed side gear which is
lower than the low-speed side gear is selected to put the vehicle ready for reacceleration
or start from standstill, thereby making it possible to smoothly accelerate or start
the vehicle from standstill.
Brief Description of the Drawings
[0024]
Fig. 1 is a schematic diagram showing a vehicle driving system according to a first
embodiment of the invention.
Fig. 2 shows diagrams illustrating a 1st EV mode, of which (a) is a speed diagram, and (b) is a diagram showing torque transmitting
conditions of the vehicle driving system.
Fig. 3 shows diagrams illustrating a 3rd EV mode, of which (a) is a speed diagram, and (b) is a diagram showing torque transmitting
conditions of the vehicle driving system.
Fig. 4 shows diagrams illustrating a regeneration in the 3rd EV mode, of which (a) is a speed diagram, and (b) is a diagram showing torque transmitting
conditions of the vehicle driving system.
Fig. 5 shows diagrams illustrating a 5th EV mode, of which (a) is a speed diagram, and (b) is a diagram showing torque transmitting
conditions of the vehicle driving system.
Fig. 6 shows diagrams illustrating a regeneration in the 5th EV mode, of which (a) is a speed diagram, and (b) is a diagram showing torque transmitting
conditions of the vehicle driving system.
Fig. 7 is a schematic diagram of an example of a brake system which is used in the
vehicle driving system of this embodiment.
Fig. 8 is a graph showing a distribution of braking force when the vehicle is stopped
by the driver who depresses a brake pedal while the vehicle is running on an engine.
Fig. 9 is a graph showing a relation between vehicle driving points and regeneration
possible regions in respective EV modes.
Fig. 10 is a graph showing a relation between braking force and vehicle speed when
downshifting is carried out in accordance with the deceleration of the vehicle during
EV running.
Fig. 11 is a graph showing a relation between braking force and vehicle speed when
wheel brakes are actuated in a cooperative fashion during downshifting carried out
in accordance with the deceleration of the vehicle during EV running.
Fig. 12 is a control flowchart of decelerating the vehicle during EV running. Fig.
13 is a graph showing a relation between braking force and vehicle speed when engine
braking is used during downshifting executed in accordance with the deceleration of
the vehicle during EV running.
Fig. 14 is a control flowchart of the downshifting using engine braking effects shown
in Fig. 13.
Fig. 15 shows diagrams showing torque transmitting conditions of the vehicle driving
system when engine braking is used during downshifting from 5th EV mode to 3rd EV mode, of which (a) shows a state in which the downshifting is made in a fifth
speed connecting position, and (b) shows a state in which the downshifting is made
in a third speed connecting position.
Fig. 16(a) is an exemplary diagram showing another example of a brake system, Fig.
16(b) is a graph showing a relation between vehicle speed and pedal effort, and Fig.
16(c) is a graph showing a distribution of braking force.
Fig. 17(a) is an exemplary diagram showing a further example of a brake system, Fig.
17(b) is a graph showing a relation between vehicle speed and pedal effort, and Fig.
17(c) is a graph showing a distribution of braking force.
Fig. 18 is a schematic diagram showing a vehicle driving system according to a second
embodiment of the invention.
Fig. 19 is a schematic diagram of a vehicle driving system described in Patent Literature
1.
Mode for Carrying out the Invention
[0025] Hereinafter, embodiments of vehicle driving systems of the invention will be described
by reference to the drawings.
<First Embodiment>
[0026] As shown in Fig. 1, a vehicle driving system 1 of a first embodiment is for driving
drive wheels DW, DW (a driven portion) via drive shafts 9, 9 of a vehicle (not shown)
and includes an internal combustion engine (hereinafter, referred to as an engine)
6 which is a drive source, an electric motor (hereinafter, referred to as a motor)
7, a transmission 20 for transmitting power to the drive wheels DW, DW, and a planetary
gear mechanism 30 as a differential reduction gear mechanism which constitutes part
of the transmission 20.
[0027] The engine 6 is a gasoline engine, for example, and a first clutch 41 (a first engaging
and disengaging unit) and a second clutch 42 (a second engaging and disengaging unit)
of the transmission 20 are provided on a crankshaft 6a of the engine 6.
[0028] The motor 7 is a three-phase brushless DC motor and has a stator 71 which includes
3n armatures 71a and a rotor 72 which is disposed so as to face the stator 71.
Each armature 71a includes an iron core 71b and a coil which is wound around the iron
core 71b and is fixed to a casing, not shown. The armatures 71a are aligned circumferentially
at almost equal intervals about a rotating shaft. The 3n coils 71c make up n sets
of three-phase coils of U-phase, V-phase and W-phase.
[0029] The rotor 72 has n permanent magnets 72a which is aligned at almost equal intervals
about the rotating shaft, and polarities of any two adjacent permanent magnets 72a
are different from each other. A fixing portion 72b which fixed each permanent magnet
72a in place has a hollow cylindrical shape which is made of a magnetically soft material.
The fixing portions 72b are disposed on an outer circumferential side of a ring gear
35 and are connected to a sun gear 32 of the planetary gear mechanism 30. By adopting
this configuration, the rotor 72 is made to rotate together with the sun gear 32 of
the planetary gear mechanism 30.
[0030] The planetary gear mechanism 30 has the sun gear 32, the ring gear 35 which is disposed
concentrically with the sun gear 32 and is disposed so as to surround the periphery
of the sun gear 32, planetary gears 34 which mesh with the sun gear 32 and the ring
gear 35, and a carrier 36 which supports the planetary gears 34 so as to rotate on
their own axes and walk around the sun gear 32 and the ring gear 35. In this way,
the sun gear 32, the ring gear 35 and the carrier 36 are made to rotate differentially
relative to each other.
[0031] A lock mechanism 61 is provided on the ring gear 35, and this lock mechanism 61 has
a synchronizing mechanism (a synchronizer mechanism) and is made to stop (lock) the
rotation of the ring gear 35.
[0032] The transmission 20 is a so-called twin-clutch type transmission which includes the
first clutch 41 and the second clutch 42, the planetary gear mechanism 30 and a plurality
of change-speed gear groups, which will be described later.
[0033] More specifically, the transmission 20 includes a first main shaft 11 (a first input
shaft) which is disposed concentrically with the crankshaft 6a of the engine 6 (a
rotating axis Al), a second main shaft 12, a connecting shaft 13, a countershaft 14
(an output/input shaft) which can rotate about a rotating axis B1 which is disposed
parallel to the rotating axis A1, a first intermediate shaft 15 which can rotate about
a rotating axis C2 which is disposed parallel to the rotating axis A1, a second intermediate
shaft 16 (a second input shaft) which can rotate about a rotating axis Dl which is
disposed parallel to the rotating axis Al, and a reverse shaft 17 which can rotate
about a rotating axis El which is disposed parallel to the rotating axis Al.
[0034] The first clutch 41 is provided on the first main shaft 11 on a side which faces
the engine 6, and the sun gear 32 of the planetary gear mechanism 30 and the rotor
72 of the motor 7 are mounted on the first main shaft 11 on an opposite side to the
side facing the engine 6.
Consequently, the first main shaft 11 is selectively connected to the crankshaft 6a
of the engine 6 by the first clutch and is connected directly to the motor 7, so that
power of the engine 6 and/or the motor is transmitted to the sun gear 32.
[0035] The second main shaft 12 is shorter than the first main shaft 11 and is hollow.
The second main shaft 12 is disposed to rotate relative to the first main shaft 11
so as to cover the periphery of a portion of the first main shaft 11 which is situated
on a side to face the engine 6. In addition, the second clutch 42 is provided on the
second main shaft 12 on a side to face the engine 6, and an idler drive gear 27a is
mounted integrally on the second main shaft 12 on an opposite side to the side facing
the engine 6. Consequently, the second main shaft 12 is connected selectively to the
crankshaft 6a of the engine 6 by the second clutch 42 so that power of the engine
6 is transmitted to the idler drive gear 27a.
[0036] The connecting shaft 13 is shorter than the first main shaft 11 and is hollow. The
connecting shaft 13 is disposed to rotate relative to the first main shaft 11 so as
to cover a portion of the first main shaft 11 which is situated on an opposite side
to a side facing the engine 6. A third speed drive gear 23a is mounted integrally
on the connecting shaft 13 on a side which faces the engine 6, and the carrier 36
of the planetary gear mechanism 30 is mounted integrally on the connecting shaft 13
on an opposite side to the side facing the engine 6. Consequently, the carrier 36
which is mounted on the connecting shaft 13 and the third speed drive gear 23a are
made to rotate together when the planetary gears 34 walk around the sun gear 32 and
the ring gear 35.
[0037] Further, a fifth speed drive gear 25a is provided on the main shaft 11 between the
third speed drive gear 23 a which is mounted on the connecting shaft 13 and the idler
drive gear 27a which is mounted on the second main shaft 12 so as to rotate relative
to the first main shaft 11. Additionally, a reverse driven gear 28b is mounted on
the first main shaft 11 so as to rotate together with the first main shaft 11. Further,
a first change-speed shifter 51 is provided between the third speed drive gear 23a
and the fifth speed drive gear 25a, the first change-speed shifter 51 being adapted
to connect the first main shaft 11 and the third speed drive gear 23a or the fifth
speed drive gear 25a or release the connection. Then, when the first change-speed
shifter 51 is engaged in a third speed connecting position, the first main shaft 11
and the third speed drive gear 23a are connected together so as to rotate together.
When the first change-speed shifter 51 is engaged in a fifth speed connecting position,
the first main shaft 11 and the fifth speed drive gear 25a are connected together
so as to rotate together. When the first change-speed shifter 51 is in a neutral position,
the first main shaft 11 rotates relative to the third speed drive gear 23a and the
fifth speed drive gear 25a. When the first main shaft 11 and the third speed drive
gear 23a rotate together, the sun gear 32 which is mounted on the first main shaft
11 and the carrier 36 which is connected to the third speed drive gear 23a by the
connecting shaft 13 rotate together, and the ring gear 35 also rotate together, whereby
the planetary gear mechanism 30 works as a unit.
[0038] . A first idler driven gear 27b is mounted integrally on the first intermediate shaft
15, and this first idler driven gear 27b meshes with the idler drive gear 27a which
is mounted on the second main shaft 12.
[0039] A second idler driven gear 27c is mounted integrally on the second intermediate shaft
16, and this second idler driven gear 27c meshes with the first idler driven gear
27b which is mounted on the first intermediate shaft. The second idler driven gear
27c makes up a first idler gear train 27A together with the idler drive gear 27a and
the first idler driven gear 27b. A second speed drive gear 22a and a fourth speed
drive gear 24a, which can rotate relative to the second intermediate shaft 16, are
provided on the second intermediate shaft 16 in positions which correspond to the
third speed drive gear 23a and the fifth speed drive gear 25a which are provided around
the first main shaft 11. Further, a second change-speed shifter 52 is provided on
the second intermediate shaft 16 between the second speed drive gear 22a and the fourth
speed drive gear 24a, and this second change-speed shifter 52 connects the second
intermediate shaft 16 and the second speed drive gear 22a or the fourth speed drive
gear 24a or releases the connection. Then, the second change-speed shifter 52 is engaged
in a second speed connecting position, the second intermediate shaft 16 and the second
speed drive gear 22a rotate together, while the second change-speed shifter 52 is
engaged in a fourth speed connecting position, the second intermediate shaft 16 and
the fourth speed drive gear 24a rotate together. When the second change-speed shifter
52 is in a neutral position, the second intermediate shaft 12 rotates relative to
the second speed drive gear 22a and the fourth speed drive gear 24a.
[0040] A first common driven gear 23b, a second common driven gear 24b, a park gear 21,
and a final gear 26a are mounted integrally on the countershaft 14 sequentially in
that order from an opposite side to a side which faces the engine 6.
Here, the first common driven gear 23b meshes with the third speed drive gear 23a
which is mounted on the connecting shaft 13 and makes up a third speed gear pair together
with the third speed drive gear 23 a. In addition, the first common driven gear 23b
meshes with the second speed drive gear 22a which is provided on the second intermediate
shaft 16 and makes up a second speed gear pair 22 together with the second speed drive
gear 22a.
The second common driven gear 24b meshes with the fifth speed drive gear 25a which
is provided on the first main shaft 11 and makes up a fifth speed gear pair 25 together
with the fifth speed drive gear 25a. The second common driven gear 24b meshes with
the fourth speed drive gear 24a which is provided on the second intermediate shaft
16 and makes up a fourth speed gear pair 24 together with the fourth speed drive gear
24a.
The final gear 26a meshes with the differential gear mechanism 8, and the differential
gear mechanism 8 is connected to the drive wheels DW, DW via the drive shafts 9, 9.
Consequently, power transmitted to the countershaft 14 is outputted from the final
gear 26a to the drive wheels DW, DW via the differential gear mechanism 8 and the
drive shafts 9. 9.
[0041] A third idler driven gear 27d is mounted integrally on the reverse shaft 17, and
this third idler driven gear 27d meshes with the first idler driven gear 27b which
is mounted on the first intermediate shaft 15. The third idler driven gear 27d makes
up a second idler gear train 27B together with the idler drive gear 27a and the first
idler driven gear 27b. A reverse drive gear 28a is provided on the reverse shaft 17
so as to rotate relative to the reverse shaft 17, and this reverse drive gear 28a
meshes with a reverse driven gear 28b which is mounted on the first main shaft 11.
The reverse drive gear 28a makes up a reverse gear train 28 together with the reverse
driven gear 28b. Further, a reverse shifter 53 is provided on an opposite side of
the reverse drive gear 28a to a side which faces the engine 6, and this reverse shifter
53 connects the reverse shaft 17 and the reverse drive gear 28a or release the connection.
Then, when the reverse shifter 53 is engaged in a reverse connecting position, the
reverse shaft 17 and the reverse drive gear 28a rotate together, while when the reverse
shifter 53 is in a neutral position, the reverse shaft 17 and the reverse drive gear
28a rotate relative to each other.
[0042] The first change-speed shifter 51, the second change-speed shifter 52 and the reverse
change-speed shifter 53 employ a clutch mechanism having a synchronizing mechanism
(a synchronizer mechanism) which makes the revolution speed of the gear match the
revolution speed of the shaft to which the gear is connected.
[0043] In the transmission 20 which is configured as has been described heretofore, an odd
speed gear group (a first gear group) made up of the third speed drive gear 23a and
the fifth speed drive gear 25a is provided on the first main shaft 11 which is one
change-speed shaft of two change-speed shafts. In addition, an even speed gear group
(a second gear group) which is made up of the second speed drive gear 22a and the
fourth speed drive gear 24a is provided on the second intermediate shaft 16 which
is the other change-speed shaft of the two change-speed shafts.
[0044] Based on the configuration that has been described heretofore, the vehicle driving
system 1 of this embodiment has the following first to fifth transmission paths.
(1) A first transmission path is a transmission path where the crankshaft 6a of the
engine 6 is connected to the drive wheels DW, DW via the first main shaft 11, the
planetary gear mechanism 30, the connecting shaft 13, the third speed gear pair 23
(the third speed drive gear 23a, the first common driven gear 23b), the countershaft
14, the final gear 26a, the differential gear mechanism 8 and the drive shafts 9,
9. Here, a reduction ratio of the planetary gear mechanism 30 is set so that engine
torque transmitted to the drive shafts DW, DW via the first transmission path corresponds
to a first speed. Namely, a reduction ratio resulting by multiplying the reduction
ratio of the planetary gear mechanism 30 by a reduction ratio of the third speed gear
pair 23 corresponds to the first speed.
[0045]
(2) A second transmission path is a transmission path where the crankshaft 6a of the
engine 6 is connected to the drive wheels DW, DW via the second main shaft 12, the
first idler gear train 27A (the idler drive gear 27a, the first idler driven gear
27b, the second idler driven gear 27c), the second intermediate shaft 16, the second
speed gear pair 22 (the second speed drive gear 22a, the first common driven gear
23b) or the fourth speed gear pair 24 (the fourth speed drive gear 24a, the second
common driven gear 24b), the countershaft 14, the final gear 26a, the differential
gear mechanism 8 and the drive shafts 9, 9.
[0046]
(3) A third transmission path is a transmission path where the crankshaft 6a of the
engine 6 is connected to the drive wheels DW, DW via the first main shaft 11, the
third speed gear pair 23 (the third speed drive gear 23a, the first common driven
gear 23b) or the fifth speed gear pair 25 (the fifth speed drive gear 25a, the second
common driven gear 24b), the countershaft 14, the final gear 26a, the differential
gear mechanism 8 and the drive shafts 9, 9 without passing by the planetary gear mechanism
30.
[0047]
(4) A fourth transmission path is a transmission path where the motor 7 is connected
to the drive wheels DW, DW via the planetary gear mechanism 30 or the third speed
gear pair 23 (the third speed drive gear 23a, the first common driven gear 23b) or
the fifth speed gear pair 25 (the fifth speed drive gear 25a, the second common driven
gear 24b), the countershaft 14, the final gear 26a, the differential gear mechanism
8 and the drive shafts 9, 9.
[0048]
(5) A fifth transmission path is a transmission path where the crankshaft 6a of the
engine 6 is connected to the drive wheels DW, DW via the second main shaft 12, the
second idler gear train 27B (the idler drive gear 27a, the first idler driven gear
27b, the third idler driven gear 27d), the reverse shaft 17, the reverse gear train
28 (the reverse drive gear 28a, the reverse driven gear 28b), the planetary gear mechanism
30, the connecting shaft 13, the third speed gear pair 23 (the third speed drive gear
23a, the first common driven gear 23b), the countershaft 14, the final gear 26a, the
differential gear mechanism 8 and the drive shafts 9, 9.
[0049] In addition, in the vehicle driving system of this embodiment, the motor 7 is connected
to a battery 3 via a power control unit (hereinafter, referred to as PDU) 2 which
controls the operation thereof, whereby an electric power supply to the motor 7 from
the battery 3 and an energy regeneration to the battery 7 are implemented via the
PDU 2. Namely, the motor 7 is driven by the electric power supplied thereto from the
battery 3 via the PDU 2. In addition, a regenerative electricity generation is implemented
by the rotation of the drive wheels DW, DW or the power of the engine 6 when the vehicle
is decelerated so as to charge the battery 3 (energy recovery). Further, the PDU 2
is connected to an electronic control unit (hereinafter, referred to as an ECU) 5.
The ECU 5 is a control unit for controlling the whole vehicle in various ways. Inputted
into the ECU 5 are an acceleration request, a braking request, engine revolution speed,
motor revolution speed, motor temperature, revolution speeds of the first and second
main shafts 11, 12, revolution speed of the countershaft 14, vehicle speed, gear position,
SOC. On the other hand, outputted from the ECU 5 are a signal controlling the engine
6, a signal controlling the motor 7, signals indicating electricity generation state,
charged state and discharged state of the battery 3, signals controlling the first
and second change-speed shifters 51, 52, a signal controlling the reverse shifter
53, and a signal controlling the locking by the lock mechanism 61. Additionally, the
ECU 5 controls a brake system 100, which will be described later and also controls
the braking of the vehicle driving system 1.
[0050] The vehicle driving system 1 which is configured as has been described heretofore
controls the engagement and disengagement of the first and second clutches 41, 42
and also controls the connecting positions of the first change-speed shifter 51, the
second change-speed shifter 52 and the reverse shifter 53 to thereby run the vehicle
at the first to fifth speeds and reverse by the engine 6. Additionally, the vehicle
driving system 1 can assist in running the vehicle or perform a regenerative operation
using the motor 7 while the vehicle is running. Further, the vehicle driving system
1 can start the engine 6 using the motor 7 or charge the battery 3 during idling.
[0051] Additionally, the vehicle driving system 1 enables an EV running by use of the motor
7. The vehicle driving system 1 includes three EV running modes. In the following
description, unless otherwise stipulated, the first and second clutches 41, 42 are
disengaged, the first and second change-speed shifter and reverse shifter 51 to 53
are in the neutral position, and the lock mechanism 61 is in a lock-off state (SYN
LOCK OFF) which permits the rotation of the ring gear 35. Hereinafter, this state
will be referred to as an initial state. In a speed diagram in Fig. 2(a), a stop position
of the motor 7 is represented by 0, an upper area than 0 represents a forward rotating
direction, a lower area than 0 represents a reverse rotating direction, the sun gear
32 is denoted by "S," the carrier 36 is denoted by "C," and the ring gear 35 is denoted
by "R." This will also be true with speed diagrams which will be described later.
Fig. 2(b) is a diagram showing torque transmitting conditions. A thick hatched arrow
indicates a flow of torque, and hatching in the arrow corresponds to hatching in arrows
indicating torque in the speed diagram. In addition, the forward rotating direction
of the motor 7 denotes a direction in which a forward torque is transmitted to the
drive wheels DW, DW via the drive shafts 9, 9, whereas the reverse rotating direction
of the motor 7 denotes a direction in which a reverse torque is transmitted to the
drive wheels DW, DW via the drive shafts 9, 9.
[0052] A first EV running mode is a 1
st EV mode which is attained from the initial state by putting the lock mechanism 61
in a lock state (SYN LOCK ON).
In this stat, when the motor 7 is driven (torque is applied in the forward rotating
direction), as shown in Fig. 2(a), the sun gear 32 of the planetary gear mechanism
30 which is connected to the rotor 72 rotates in the forward rotating direction.
As this occurs, as shown in Fig. 2(b), since the first and second clutches 41, 42
are disengaged, power transmitted to the sun gear 32 is never transmitted from the
first main shaft 11 to the crankshaft 6a of the engine 6. Additionally, since the
locking by the lock mechanism 61 is not implemented, motor torque transmitted to the
sun gear 32 is transmitted to the carrier 36 and is then transmitted to the drive
wheels DW, DW by way of the fourth transmission path which passes by way of the planetary
gear mechanism 30. As this occurs, since the ring gear 35 is locked, the sun gear
32 rotates at a higher revolution speed than the carrier 36 while maintaining a collinear
relation shown in Fig. 2(a) due to the characteristics of the planetary gear mechanism
30. Namely, the motor torque is transmitted which is reduced by the planetary gear
mechanism 30.
[0053] A second EV running mode is a 3
rd EV mode which is attained from the initial state by engaging the first change-speed
shifter 51 in the third speed connecting position from the neutral position. As has
been described before, by engaging the first change-speed shifter 51 in the third
speed connecting position, the planetary gear mechanism 30 is made into the single
unit.
In this state, when the motor 7 is driven (torque is applied in the forward rotating
direction), the planetary gear mechanism 30 which is connected to the rotor 72 rotates
in the forward rotating direction as a unit. As this occurs, since the first and second
clutches 41, 42 are disengaged, the power transmitted to the sun gear 32 is never
transmitted from the first main shaft 11 to the crankshaft 6a of the engine 6. Then,
the motor torque is transmitted to the drive wheels DW, DW by way of the fourth transmission
which passes by way of the third speed gear pair 23.
[0054] When regeneration is implemented while the vehicle is running on the 3
rd EV running mode, as shown in Fig. 4, regenerative torque is applied to the motor
7 in a direction in which the revolution speed of the rotor 72 is reduced, that is,
in a reverse direction, whereby electricity can be generated in the motor 7 while
applying a braking force to the vehicle, thereby making it possible to charge the
battery 3.
[0055] A third EV running mode is a 5
th EV mode which is attained from the initial state by engaging the first change-speed
shifter 51 in the fifth speed connecting position from the neutral position.
In this state, when the motor 7 is driven (torque is applied in the forward rotating
direction, the sun gear 32 of the planetary gear mechanism 30 which is connected to
the rotor 72 rotates in the forward rotating direction as shown in Fig. 5(b). As this
occurs, as shown in Fig. 5(b), since the first and second clutches 41, 42 are disengaged,
the power transmitted to the sun gear 32 in never transmitted from the first main
shaft 11 to the crankshaft 6a of the engine 6. Then, the motor torque is transmitted
to the drive wheels DW, DW by way of the fourth transmission path which passes by
way of the fifth gear pair 25. As this occurs, the sun gear 32 rotates at the revolution
speed of the motor 7 and the carrier 36 rotates while being connected to the countershaft
14 by way of the third speed gear train 23. Therefore, a predetermined differential
rotation is generated between the sun gear 32 and the carrier 36, and the ring gear
35 rotates at a higher revolution speed than the carrier 36 while maintaining a collinear
relation shown in Fig. 5(a) due to the characteristics of the planetary gear mechanism
30.
[0056] When regeneration is implemented while the vehicle is running on the 5
th EV running mode, as shown in Fig. 6, regenerative torque is applied to the motor
7 in the direction in which the revolution speed of the rotor 72 is reduced, that
is, in the reverse direction, whereby electricity can be generated in the motor 7
while applying a braking force to the vehicle, thereby making it possible to charge
the battery 3.
[0057] Following this, an example of a brake system which is used in the vehicle driving
system 1 of the embodiment will be described.
As shown in Fig. 7, the brake system 100 includes a tandem type master cylinder M,
a hydraulic booster 113 which regulates the hydraulic pressure in a hydraulic pressure
generation source 112 in accordance with brake effort inputted from a brake pedal
111 which is a brake control member for application to the master cylinder M, and
a stroke simulator 114 which is interposed between the brake pedal 111 I and the hydraulic
booster 113.
[0058] A cylinder body 116 of the master cylinder M is formed into a bottomed cylindrical
shape which is closed at a front end thereof, and a rear end of the cylinder body
116 is connected to a front end of a casing 117 that the hydraulic booster 113 3 includes.
The rear end of the cylinder body 16 is fitted in a front portion of the casing 117
fluidly tightly. A separator 18, a first sleeve 119 and a second sleeve 120 which
are fitted in the casing 117 fluidly tightly are held between the rear end of the
cylinder body 116 and the casing 117 with the first sleeve 119 held between the separator
118 8 and the second sleeve 120.
[0059] A first cylinder bore 121 is formed in the cylinder body 116, and the first cylinder
bore 121 is closed at a front end thereof. The master cylinder M is made up of a rear
master piston 123 and a front master piston 124. The rear master piston 123 faces
a booster hydraulic chamber 122 on the back thereof and is biased rearwards by a spring.
The rear master piston 123 is slidably fitted in the first cylinder bore 121. The
front master piston 124 is disposed in front of the rear master piston 123 while being
biased rearwards by a spring and is slidably fitted in the first cylinder bore 121.
A rear output hydraulic chamber 125 is formed between the rear master piston 123 and
the front master piston 124, and a front output hydraulic chamber 126 is formed between
a front end closed portion of the cylinder body 116 and the front master piston 124.
[0060] A rear output port 127 and a front output port 128 are provided in the cylinder
body 116. The rear output port 127 communicates with a rear output hydraulic chamber
125, and the front output port 128 communicates with a front output hydraulic chamber
126. Further, a rear return spring 129 is provided within the rear output hydraulic
chamber 125 between the rear master piston 123 and the front master piston 124 in
a compressed state, the rear return spring 129 being adapted to bias the rear master
pin 123 to the rear. In addition, a front return spring 130 is provided within the
front output hydraulic chamber 126 between the front closed end of the cylinder body116
and the front master piston 124 in a compressed state, the front return spring 130
being adapted to bias the front master piston 124 to the rear.
[0061] A reservoir 131 is attached to the master cylinder M. A first, second and third fluid
reserving chambers 131a, 131b, 131c are formed in the reservoir 131 so as to be divided
independently from each other. A rear connecting cylindrical portion 132 having a
cylindrical shape and a front connecting cylindrical portion 133 having a cylindrical
shape are provided integrally on the master cylinder M so as to project upwards in
positions which are spaced apart from each other in an axial direction. The rear connecting
cylindrical portion 132 communicates with the second fluid reserving chamber 131b,and
the front connecting cylindrical portion communicates with the first fluid reserving
chamber 131a.
[0062] A center valve 134 is mounted on the rear master piston 123 so as to cause the rear
output hydraulic chamber 125 to communicate with the second fluid reserving chamber
131b when the rear master piston 123 returns to a withdrawal limit position. A center
valve 135 is mounted on the front master piston 124 so as to cause the front output
hydraulic chamber 126 to communicate with the first fluid reserving chamber 131a when
the front master piston 124 returns to a withdrawal limit position.
[0063] The rear output port 127 of the master cylinder M is connected to a right front wheel
brake B1 and a left rear wheel brake B2 via a hydraulic modulator 136. The front output
port 128 is connected to a left front wheel brake B3 and a right rear wheel brake
B4 via the hydraulic modulator 136. Thus, the hydraulic modulator 136 is a conventionally
known hydraulic modulator which can execute an automatic brake control such as an
anti-lock brake control executed when the brakes are applied and a traction control
executed when the brakes are not applied by controlling freely a brake pressure which
is outputted from the rear and front output ports 127, 128.
[0064] The hydraulic booster 113 includes a cylindrical backup piston 138, a pressure regulator
valve device 139 which is incorporated in the backup piston 138, a control piston
141, a first reaction piston 142, and a second reaction piston 143. The backup piston
138 faces the booster hydraulic chamber 122 at a front end thereof so as to push directly
the rear master piston 123 of the master cylinder M from the rear thereof. The backup
piston 138 is slidably fitted in the separator 118 and the second sleeve 120. The
control piston 141 actuates the pressure regulator valve device 139 so as to regulate
the pressure by balancing a reaction force based on the hydraulic pressure in a booster
hydraulic pressure generating chamber 140 which is connected to the booster hydraulic
chamber 122 with a brake application input which is inputted from the brake pedal
111. The first reaction piston 142 is interposed between the pressure regulator valve
device 139 and the control piston 141 so as to add a reaction force based on the hydraulic
pressure in the booster hydraulic pressure generation chamber 140 to the control piston
141. The second reaction piston 143 is interposed between the backup piston 138 and
the first reaction piston 142 so as to apply an output hydraulic pressure of the hydraulic
pressure generation source 112 and a reaction force by a reaction spring 144 in addition
to a reaction force from the first reaction piston 142 to the control piston 141 when
the brake application input by the brake pedal 111 is increased.
[0065] A connecting fluid path 145 which communicates with the booster hydraulic chamber
122, an input port 146 which is connected to the hydraulic pressure generation source
112, an output fluid path 147 which communicates with the hydraulic pressure generation
chamber 140, and a release port 148 which communicates with the release chamber 149
which is formed within the casing 117 at the rear of the second sleeve 120 are provided
sequentially in that order from the front so as to be spaced apart from each other.
[0066] The hydraulic pressure generation source 112 is connected to the input port 146.
This hydraulic pressure generation source 112 includes a pump 151 which pumps up a
working fluid from the third fluid reserving chamber 131c of the reservoir 131, and
an accumulator which is connected to a discharge side of the pump 151. The operation
of the pump 151 is controlled in accordance with the hydraulic pressure of the accumulator
152 which is detected by a hydraulic pressure sensor 53 within the casing 17, and
a high constant hydraulic pressure is supplied to the input port 146 from the hydraulic
pressure generation source 112. In addition, the release port 148 is connected to
the third fluid reserving chamber 131c of the reservoir 131.
[0067] The pressure regulator valve device 139 is made up of a pressure increasing valve
which is interposed between the input port 146 and the booster hydraulic pressure
generation chamber 140 and a pressure reducing valve which is interposed between the
booster hydraulic pressure generation chamber 140 and the release chamber 149. Thus,
a booster hydraulic pressure which is obtained by regulating the hydraulic pressure
in the hydraulic pressure generation source 112 is generated in the booster hydraulic
pressure generation chamber 140 by opening or closing the pressure increasing valve
in response to the depression of the brake pedal 111.
[0068] In the hydraulic booster 113 configured as has been described above, brake application
input is inputted from the brake pedal 111 to the control piston 141 via the stroke
simulator 114, whereby a forward pressure is applied to the first reaction piston
142 from the control piston 141. Thus, in such a state that a forward traveling amount
of the control piston 141 relative to the backup piston 138 is less than a predetermined
value, only the first reaction piston 142 is in abutment with the control piston 141.
The pressure reducing valve of the pressure regulator valve device 139 is closed as
the first reaction piston 142 advances, whereby a communication between the booster
hydraulic pressure generation chamber 140 and the release chamber 149 is cut off.
When the control piston 141 and the first reaction piston 142 advance further, the
pressure increasing valve of the pressure regulator valve device 139 is opened.
[0069] The hydraulic pressure of the booster hydraulic pressure generation chamber 140 is
applied to a front end of the first reaction piston 142 with the pressure reducing
valve closed. When the first reaction piston 142 and the control piston 141 withdraw
so that the brake application input from the brake pedal 111 is balanced with the
hydraulic pressure based on the hydraulic pressure in the booster hydraulic pressure
generation chamber 140, the pressure reducing valve is opened and the pressure increasing
valve is closed. By repeating the opening and closing of the pressure increasing valve
and the pressure reducing valve, the output hydraulic pressure of the hydraulic pressure
generation source 112 is regulated to a booster hydraulic pressure which corresponds
to the brake application input from the brake pedal 111 for application to the booster
hydraulic pressure generation chamber 140. In addition, when the forward traveling
amount of the control piston 141 relative to the backup piston 138 reaches and exceeds
the predetermined value, not only the first reaction piston 142 but also the second
reaction piston 143 are brought into abutment with the control piston 141, whereby
not only a hydraulic pressure which pushes the second reaction piston 143 to the rear
by virtue of the hydraulic pressure from the hydraulic pressure generation source
112 but also the spring force of the reaction spring 144 are added as a reaction force,
this increasing the reaction force acting on the control piston 141.
[0070] The connecting fluid path 145, which is provided in the casing 117 so as to communicate
with the booster hydraulic chamber 122, is connected to the hydraulic pressure generation
source 112 via an automatic brake pressure applying electromagnetic valve 154 which
is a normally closed linear solenoid valve and is connected to the third fluid reserving
chamber 131c of the reservoir 131 via a regeneration cooperative pressure reducing
electromagnetic valve 155 which is a normally closed linear solenoid valve. Namely,
the normally closed automatic brake pressure applying electromagnetic valve 154 is
interposed between the booster hydraulic chamber 122 and the hydraulic pressure generation
source 112, and the normally closed regeneration cooperative pressure reducing electromagnetic
valve 155 is interposed between the booster hydraulic chamber 122 and the reservoir
131.
[0071] In addition, the output fluid path 147, which communicates with the booster hydraulic
pressure generation chamber 140, is connected to the connecting fluid path 145 via
an automatic brake pressure reducing electromagnetic valve 156 and a regeneration
cooperative pressure applying electromagnetic valve 157 which are connected in series.
Both the automatic brake pressure reducing electromagnetic valve 256 and the regeneration
cooperative pressure applying electromagnetic valve 157 are a normally open linear
solenoid valve.
[0072] A first one-way valve 158 is connected in parallel to the automatic brake pressure
reducing electromagnetic valve 156, and this first one-way valve 158 permits a flow
of working fluid from the output fluid path 147 to the connecting fluid path 145.
In addition, a second one-way valve 159 is connected in parallel to the regeneration
cooperative pressure applying electromagnetic valve 157, and this second one-way valve
159 permits a flow of working fluid from the connecting fluid path to the output fluid
path 147.
[0073] Namely, the automatic brake pressure reducing electromagnetic valve 156, to which
the first one-way valve 158 is connected in parallel, and the regeneration cooperative
pressure applying electromagnetic valve 159, to which the second one-way valve 159
is connected in parallel, are interposed between the booster hydraulic pressure generation
chamber 140 and the booster hydraulic chamber 122.
[0074] Moreover, a brake application amount detecting hydraulic sensor 160 is connected
between the output fluid path 147 and the automatic brake pressure reducing electromagnetic
valve 156. An automatic brake feedback controlling hydraulic sensor 161 is connected
between the regeneration cooperative pressure applying electromagnetic valve 157 and
the connecting fluid path 145.
[0075] In this way, the automatic brake pressure applying electromagnetic valve 154 is interposed
between the hydraulic pressure generation source 112 and the booster hydraulic chamber
122. The automatic brake pressure reducing electromagnetic valve 156 and the first
one-way valve 158, which is connected in parallel to the automatic brake pressure
reducing valve 156 so as to permit the flow of brake fluid from the booster hydraulic
pressure generation chamber 140 to the booster hydraulic chamber 122, are interposed
between the booster hydraulic pressure generation chamber 140 and the booster hydraulic
chamber 122. Thus, when the brake pedal 111 is not depressed, that is, when the pressure
regulator valve device 139 is not operated, too, by controlling the automatic brake
pressure applying electromagnetic vale 154 and the automatic brake pressure reducing
electromagnet valve 156 to be opened or closed so as to regulate the hydraulic pressure
of the booster hydraulic chamber 122, an automatic brake control can be performed
in which with no brakes applied, brake hydraulic pressures are caused to be applied
to the wheel brakes B1 to B4. Moreover, when the pressure regulator valve 139 is actuated
to generate a higher hydraulic pressure than the hydraulic pressure in the booster
hydraulic chamber 112 in the booster hydraulic pressure generation chamber 140 by
depressing the brake pedal 111 with the automatic brake pressure reducing electromagnetic
valve 156 closed while an automatic brake is applied, the hydraulic pressure in the
booster hydraulic pressure generation chamber 140 can be caused to be applied to the
booster hydraulic chamber 122 via the first one-way valve 158, whereby the master
cylinder M can be actuated likewise the normal brake application.
[0076] In addition, the regeneration operative pressure reducing electromagnetic valve 155
is interposed between the booster hydraulic chamber 122 and the reservoir 131, and
the regeneration cooperative pressure applying electromagnetic valve 157 and the second
one-way valve 159, which is connected in parallel to the regeneration cooperative
pressure applying electromagnetic valve 157 so as to permit the flow of brake fluid
from the booster hydraulic chamber 122 to the booster hydraulic pressure generation
chamber 140, are interposed between the booster hydraulic pressure generation chamber
140 and the booster hydraulic chamber 122. Therefore, by controlling the regeneration
cooperative pressure applying electromagnetic valve 157 and the regeneration cooperative
pressure reducing electromagnetic valve 155 to be opened and closed so as to regulate
the hydraulic pressure in the booster hydraulic chamber 122 during regeneration with
the brakes applied, a brake hydraulic pressure which is offset from the normal brake
application can be outputted from the master cylinder M. When the brake pedal 111
is released with the regeneration cooperative pressure applying electromagnetic valve
157 closed, the hydraulic pressure in the booster hydraulic chamber 122 can be relieved
to the reservoir 131 via the second one-way valve 159.
[0077] The stroke simulator 114 includes an input piston 162 which is fitted in the control
piston 141 fluidly tightly and slidably in an axial direction and a spring device
163 which is interposed between the input piston 162 and the control piston 141 and
is incorporated in the control piston 141.
[0078] An input rod 64 which is connected to the brake pedal 111 is connected to the input
piston 162 at a front end portion thereof so as to move from side to side. Namely,
brake effort according to the depression of the brake pedal 111 is inputted into the
input piston 162 via the input rod 64, and the input piston 162 operates to advance
in accordance with the inputted brake effort.
[0079] The spring device 163 includes an elastic member 165 which is formed into a cylindrical
shape using an elastic material such as a rubber and a metallic coil spring 166 of
which a spring load is set smaller than the elastic member 165. The elastic member
165 and the coil spring 166 are interposed in series between the input piston 162
and the control piston 141 so that a spring force exhibited by the coil spring 166
is applied to the control piston 141 in an initial stage of depression of the brake
pedal 111 and the elastic member 165 starts to be elastically deformed after the application
of the spring force of the coil spring 166 to the control piston 141 is completed.
[0080] A rear end portion of a boots 167 which covers a projecting portion from the casing
117 of the control piston 141 is mounted on the input rod 64, and a front end portion
of the boots 167 is mounted on a rear end portion of the casing 117.
[0081] In the brake system 100 configured as has been described heretofore, the ECU 5 controls
the automatic brake pressure applying electromagnetic valve 154 and the automatic
brake pressure reducing electromagnetic valve 156 to be opened and closed and also
controls the regeneration cooperative pressure reducing electromagnetic valve 155
and the regeneration cooperative pressure applying electromagnetic valve 157 to be
opened and closed. By this control, even when no brakes are applied with the brake
pedal 111 not depressed by the driver, not only can an automatic brake control be
executed in which brake hydraulic pressures are applied to the wheel brakes B1 to
B4, but also a so-called regeneration cooperative control can be executed in which
a brake torque is made to work in the brake system 100 which is obtained by subtracting
a regenerative brake torque from a target brake torque based on the regenerative brake
torque which varies in accordance with an amount of electricity generated by the motor
7.
[0082] Fig. 8 shows a distribution of braking force in the brake system 100 when the driver
stops the vehicle running on the engine by depressing the brake pedal. In this brake
system 100, engine braking is attained by engine friction and a braking force is generated
as a result of executing a predetermined amount of brake OFF regeneration in the motor
7 at a point in time when the driver releases an accelerator pedal (not shown). Then,
when the driver depresses the brake pedal 111, a regenerative brake (brake ON regeneration)
corresponding to a regeneration limit calculated by the ECU 5 is applied in the motor
7. This generates a braking force, and in case the braking force generated by the
brake ON regeneration is insufficient to meet a target brake torque, the insufficient
braking force is compensated for by a friction braking force generated by the wheel
brakes B1 to B4 of the brake system 100. Then, when the vehicle is slowed down to
a predetermined vehicle speed Vc, the regenerative braking amount by the motor 7 is
reduced, while the frictional braking amount by the wheel brakes B1 to B4 of the brake
system 100 is increased. When the vehicle is slowed down further to a predetermined
vehicle speed Vd, the first and second clutches 41, 42 (starter clutches) are disengaged
to thereby stop the regeneration. Finally, the vehicle is stopped by frictional braking
effect produced by the wheel brakes B1 to B4 of the brake system 100.
[0083] Thus, as has been described heretofore, according to the vehicle driving system of
the embodiment, the regeneration amount can be increased in accordance with the pedal
effort applied to the brake pedal 111. Then, the hydraulic pressure of the master
cylinder M is controlled for the first time after the regeneration amount reaches
the regeneration limit so as to ensure the braking force by the brakes. Therefore,
the vehicle can be slowed down by making full use of the regeneration of the motor
7.
[0084] Following this, a regeneration control during EV running will be described.
As shown in Fig. 9, a regeneration possible region in the 5
th EV mode is situated in a low torque, high revolution speed region. A regeneration
possible region in the 3
rd EV mode is situated in a high torque, low revolution speed region. A regeneration
possible region in the 1
st EV mode is situated in a high torque, low revolution speed region. Consequently,
when the vehicle comes to a standstill after the vehicle has run at high speeds in
the 5
th EV mode, in the 5
th EV mode, the regenerative generation cannot be executed by the motor 7 after the
vehicle has been slowed down to the predetermined vehicle speed, resulting in a state
in which electricity generation cannot be executed by the motor 7 by making effective
use of regenerative energy.
[0085] Then, it is considered to slow down the vehicle with the braking force produced by
the wheel brakes B1 to B4 of the brake system 100 in regions out of the regeneration
possible region in the 5
th EV mode. However, in this case, the braking energy cannot be made effective use of.
Further, when reaccelerating the vehicle, the vehicle is reaccelerated in the 5
th EV mode, and therefore, a required driving torque cannot be obtained, and the vehicle
is slow to be accelerated. On the other hand, it is considered to downshift the transmission
from the 5
th EV mode to the 3
rd EV mode and to the 1
st EV mode. When downshifting from the 5
th EV mode to the 3
rd EV mode, a zero torque control of the motor 7 needs to be executed while the first
change-speed shifter 51, which is now engaged in the fifth speed connecting position,
is engaged in the third speed connecting position. Further, when downshifting from
the 3
rd EV mode to the 1
st EV mode, the zero torque control of the motor 7 needs to be executed while the first
change-speed shifter 51, which is now engaged in the third speed connecting position,
is shifted into the neutral position and the lock mechanism 61 is put in the LOCK
ON state from the LOCK OFF state. However, as shown in Fig. 10, this downshifting
has a problem that the braking force of the vehicle cannot be ensured during the zero
torque control of the motor 7.
[0086] Then, in the vehicle driving system 1 of the embodiment, in downshifting from the
5
th EV mode to the 3
rd EV mode, the aforesaid automatic brake control is executed in which the loss of braking
force occurring while the first change-speed shifter 51, which is now engaged in the
fifth speed connecting position, is engaged in the third speed connecting position
is compensated for by the braking force by the wheel brakes B1 to B4 of the brake
system 100.
[0087] To describe this gear change control by reference to Figs. 11 and 12, regeneration
is executed in the 5
th EV mode with the accelerator pedal released or OFF (SO1). Then, the regenerative
torque of the motor 7 is gradually lost, while the wheel brakes B1 to B4 of the brake
system 100 are actuated so as to increase gradually the braking force so as to maintain
a predetermined braking force, when the vehicle speed is slowed down to Va (S02).
Then, in such a state that the regenerative torque is lost completely (in such a state
that the braking force is ensured only by the friction brake), downshifting is executed
by engaging the first change-speed shifter 51, which is now engaged in the fifth speed
connecting position, in the third speed connecting position (S03). Following this,
the regeneration is executed in the 3
rd EV mode while increasing gradually the regenerative torque of the motor 7, and at
the same time, the wheel brakes B1 to B4 of the brake system 100 are operated so as
to reduce gradually the braking force so as to maintain the predetermined braking
force (S04). The wheel brakes B1 to B4 of the brake system 100 are released so as
to cut off the braking force and the regeneration is executed in the 3
rd EV mode after the braking force of the motor 7 reaches a predetermined braking force
in the 3
rd EV mode (S05). Further, when the vehicle speed is slowed down to Vb, the regenerative
torque of the motor 7 is gradually lost, while the wheel brakes B1 to B4 of the brake
system 100 are actuated to increase gradually the braking force so as to maintain
the predetermined braking force (S06). When slowing down the vehicle which is slowed
down to a vehicle speed Vf or slower, a required braking force is not available from
the regeneration even in the event that the transmission is downshifted to the 1
st EV mode. Therefore, the vehicle is stopped by the braking force of the wheel brakes
B1 to B4 of the brake system 100 (S07). During this time, the first change-speed shifter
51, which is engaged in the third speed connecting position, is shifted to the neutral
position, and the lock mechanism 61 is put in the LOCK ON state from the LOCK OFF
state, whereby the vehicle is now shifted into the 1
st EV mode so as to be ready for reacceleration.
[0088] According to the vehicle driving system 1 of this embodiment that has been described
heretofore, when the vehicle is decelerated while running on the 5
th EV mode by selecting the fifth speed drive gear 25a, the wheel brakes B1 to B4 of
the brake system 100 are operated in a cooperative fashion so as to compensate for
a reduction in regenerative braking force of the motor 7 while downshifting is executed
from the fifth speed drive gear 25a to the third speed drive gear 23a by the first
change-speed shifter 51 with regeneration executed by the motor 7, that is, while
downshifting is executed from the 5
th EV mode to the 3
rd EV mode with regeneration executed by the motor 7, thereby making it possible to
ensure the braking force during downshifting. Consequently, energy which is conventionally
discharged as thermal energy while the braking force is generated by the wheel brakes
can be made effective use of as regenerative energy. In addition, the vehicle is slowed
down in accordance with the vehicle speed, and therefore, when reaccelerating the
vehicle, the vehicle can be reaccelerated smoothly.
[0089] In addition, when the required regeneration cannot be obtained after the regeneration
is executed on the third speed drive gear 23a, downshifting is executed from the 3
rd EV mode to the 1
st EV mode so as to be ready for reacceleration, thereby making it possible to reaccelerate
the vehicle smoothly when it is reaccelerated.
[0090] Additionally, in place of the wheel brakes B1 to B4 of the brake system 100 being
controlled so as to compensate for the loss of braking force which occurs during downshifting
with regeneration executed, the loss of braking force may be prevented by making use
of engine braking effects.
[0091] Referring to Figs. 13 and 14, this gear change control will be described specifically.
Regeneration is executed in the 5
th EV mode in such a state that the accelerator pedal, not shown, is released or OFF
during EV running on the 5
th EV mode (S11). Then, when the vehicle speed is lowered to Va', the first clutch 41
is engaged so as to start the engine 6 while regeneration is executed (S12). After
the engine 6 has been started, the first clutch 41 is disengaged, and the second change-speed
shifter 52 is shifted from a neutral position to be engaged in a fourth speed connecting
position (S13). In this state, the first and second clutches 41, 42 are released,
and therefore, the engine 6 is disengaged. Then, the second clutch 42 is gradually
engaged to attain engine braking while reducing the regeneration amount so as to maintain
the braking force (S14). Fig. 14(a) shows a state in which engine braking is attained
in such a state that the first clutch 41 is disengaged while the second clutch 42
is engaged and the second change-speed shifter 52 is engaged in the fourth speed connecting
position with the first change-speed shifter 51 left engaged in the fifth speed connecting
position. Then, after the second clutch 42 is engaged completely, the first change-speed
shifter 51, which is now engaged in the fifth speed connecting position, is engaged
(pre-shifted) in the third speed connecting position to thereby execute downshifting
(S15). Fig. 11(b) shows a state in which the first change-speed shifter 51 is engaged
in the third speed connecting position from the fifth speed connecting position from
the state shown in Fig. 11(a). Following this, the second clutch 42, which is now
engaged, is gradually disengaged while increasing the regeneration amount in the 3
rd EV mode so as to maintain the braking force (S16). Then, after the second clutch
42 is completely disengaged, the engine 6 is stopped, and the regeneration continues
in the 3
rd EV mode (S17). When the vehicle speed is lowered further to Vb', the regenerative
torque of the motor 7 is gradually lost so as to execute the zero torque control (S18).
A vehicle speed Vf' is a vehicle speed at which the required regeneration cannot be
obtained in the 3
rd EV mode. As to the braking at a vehicle speed Vf or slower, the required braking
force cannot be obtained from regeneration even in the event that the vehicle is slowed
down to the 1
st EV mode. Therefore, the vehicle is stopped with a braking force of a mechanical brake
105, which will be described later, as required by the intention of the driver. During
this time, the first change-speed shifter 51, which is engaged in the third speed
connecting position, is shifted to the neutral position, and the lock mechanism 61
is put in the LOCK ON state from the LOCK OFF state, whereby downshifting is executed
to 1
st EV mode so as to be ready for reacceleration.
[0092] A brake system 100A shown in Fig. 16 may be used for the gear change described above.
As shown in Fig. 16(a), the brake system 100A includes a brake pedal 101, a brake
switch 103 which detects a depression of the brake pedal 101, a tandem type master
cylinder 104 which applies a braking hydraulic pressure in accordance with a brake
application amount inputted from the brake pedal 101, the mechanical brake 105, and
a brake line 106 along which the hydraulic pressure of the master cylinder 104 is
supplied to the mechanical brake 105. The mechanical brake 105 is made up of a known
mechanical brake which is controlled by a hydraulic pressure of a disk brake or a
drum brake. An ABS mechanism 107 is provided on the brake line 106 which prevents
respective road wheels from being locked when brakes are applied.
[0093] In the brake system 100A, when stopping the vehicle which runs on engine, as shown
in Figs. 16(b) and 16(c), engine braking is attained by engine friction and a braking
force is generated as a result of executing a predetermined amount of brake OFF regeneration
in the motor 7 at a point in time when the driver releases the accelerator pedal 101.
Then, when the driver depresses the brake pedal 101, the brake switch 103 detects
the depression of the brake pedal 101, and a predetermined amount of brake ON regeneration,
which is determined in advance, is executed in the motor 7 to generate a braking force,
and a braking hydraulic pressure corresponding to the depression amount of the brake
pedal 101 is supplied to the mechanical brake 105, whereby the mechanical brake 105
is actuated. Then, when the vehicle is slowed down to reach the predetermined vehicle
speed Vc, the regenerative torque of the motor 7 is gradually lost. When the vehicle
is slowed down further to the predetermined vehicle speed Vd, the first and second
clutches 41, 42 (starter clutches) are disengaged. Finally, the vehicle is stopped
by frictional braking effect produced by the mechanical brake 105.
[0094] Additionally, a brake system 100B shown in Fig. 17 may be used.
As shown in Fig. 17(a), the brake system 100B includes a brake pedal 101, a brake
switch 103 which detects a depression of the brake pedal 101, a tandem type master
cylinder 104 which applies a braking hydraulic pressure in accordance with a brake
application amount inputted from the brake pedal 101, a master cylinder pressure sensor
108 which detects a hydraulic pressure in the master cylinder 104, a mechanical brake
105, and a brake line 106 along which the hydraulic pressure of the master cylinder
104 is supplied to the mechanical brake 105. Likewise the brake system 100 that has
been described before, the mechanical brake 105 is made up of a known mechanical brake
which is controlled by a hydraulic pressure of a disk brake or a drum brake. An ABS
mechanism 107 is provided on the brake line 106 which prevents respective road wheels
from being locked when brakes are applied.
[0095] The brake system 100B is similar to the brake system 100A that has been described
before in the following point. When stopping the vehicle which runs on engine, as
shown in Figs. 17(b) and 17(c), engine braking is attained by engine friction and
a braking force is generated as a result of executing a predetermined amount of brake
OFF regeneration in the motor 7 at a point in time when the driver releases the accelerator
pedal 101, whereby the vehicle speed is reduced. However, in this brake system 100B,
when the brake switch 103 detects the depression of the brake pedal 101, a predetermined
amount of brake ON regeneration is executed in the motor 7 to which a predetermined
regeneration amount is added in accordance with the master cylinder pressure detected
by the master cylinder pressure sensor 108. In addition, a braking hydraulic pressure
corresponding to the depression amount of the brake pedal 101 is supplied to the mechanical
brake 105, whereby the mechanical brake 105 is actuated. Then, when the vehicle is
slowed down to reach the predetermined vehicle speed Vc, the regenerative torque of
the motor 7 is gradually lost. When the vehicle is slowed down further to the predetermined
vehicle speed Vd, the first and second clutches 41, 42 are disengaged. Finally, the
vehicle is stopped by frictional braking effect produced by the mechanical brake 105.
[0096] In this brake system 100B, the predetermined amount of brake ON regeneration is executed
in the motor 7 to which the predetermined regeneration amount is added in accordance
with the master cylinder pressure detected by the master cylinder pressure sensor
108. However, the invention is not limited thereto. Hence, a stroke sensor may be
used in place of the master cylinder sensor 108 so as to add a predetermined regeneration
amount in accordance with a stroke detected by the stroke sensor.
[0097] According to the vehicle driving system 1 of this embodiment that has been described
heretofore, when the vehicle is decelerated while running on the 5
th EV mode by selecting the fifth speed drive gear 25a, the engine 6 is started, and
the second clutch 42 is engaged in such a state that the four speed drive gear 24a
is selected by the second change-speed shifter 52 while downshifting is executed from
the fifth speed drive gear 25a to the third speed drive gear 23a by the first change-speed
shifter 51 with regeneration executed by the motor 7, that is, while downshifting
is executed from the 5
th EV mode to the 3
rd EV mode with regeneration executed by the motor 7, thereby making it possible to
ensure the braking force during downshifting. Consequently, energy which is conventionally
discharged as thermal energy while the braking force is generated by the wheel brakes
can be made effective use of as regenerative energy. In addition, the vehicle is slowed
down in accordance with the vehicle speed, and therefore, when reaccelerating the
vehicle, the vehicle can be reaccelerated smoothly.
[0098] In addition, when the required regeneration cannot be obtained after the regeneration
is executed on the third speed drive gear 23a, downshifting is executed from the 3
rd EV mode to the 1
st EV mode so as to be ready for reacceleration, thereby making it possible to reaccelerate
the vehicle smoothly when it is reaccelerated.
<Second Embodiment>
[0099] Next, a vehicle driving system according to a second embodiment will be described
by reference to Fig. 18. A vehicle driving system 1A differs from the vehicle driving
system 1 in that a transmission 20A includes a six speed gear pair 96 and a seventh
speed gear pair 97 in addition to a planetary gear mechanism 30 and second to fifth
speed gear pairs 22 to 25. Hereinafter, the vehicle driving system 1A will be described
by referring only to the different feature from the vehicle driving system 1 that
has been described before.
[0100] A seventh speed drive gear 97a is provided on a first main shaft 11 between a third
speed drive gear 23a and a fifth speed drive gear 25a so as to rotate relative to
the ' first main shaft 11. In addition, a first change-speed shifter 51A is provided
between the third speed drive gear 23a and the seventh speed drive tear 97a, this
first change-speed shifter 51 A being adapted to connect the first main shaft 11 and
the third speed drive gear 23a or the seventh speed drive gear 97a or release the
connection. A third change-speed shifter 51B is provided between the seventh speed
drive gear 97a and the fifth speed drive gear 25a, this third change-speed shifter
51B being adapted to connect the first main shaft 11 and the fifth speed drive gear
25a or release the connection. Then, when the first change-speed shifter 51A is engaged
in a third speed connecting position, the first main shaft 11 and the third speed
drive gear 23a are connected together to rotate together. When the first change-speed
shifter 51A is engaged in a seventh speed connecting position, the first main shaft
11 and the seventh speed drive gear 97a rotate together. When the first change-speed
shifter 51 A is in a neutral position, the first main shaft 11 rotates relative to
the third speed drive gear 23a and the seventh speed drive gear 97a. Additionally,
when the third change-speed shifter 5 1 B is engaged in a fifth speed connecting position,
the first main shaft 11 and the fifth speed drive gear 25a are connected together
to rotate together. When the third change-speed shifter 5 1 B is in a neutral position,
the first main shaft 11 rotates relative to the fifth speed drive gear 25a.
[0101] A sixth speed drive gear 96a is provided on a second intermediate shaft 16 between
a second speed drive gear 22a and a fourth speed drive gear 24a so as to rotate relative
to the second intermediate shaft 16. Additionally, a second change-speed shifter 52A
is provided between the second speed drive gear 22a and the sixth speed drive gear
96a, this second change-speed shifter 52A being adapted to connect the second intermediate
shaft 16 and the second speed drive gear 22a or the sixth speed drive gear 96a together
or release the connection. A fourth change-speed shifter 52B is provided between the
sixth speed drive gear 96a and the fourth speed drive gear 24a, this fourth change-speed
shifter 52B being adapted to connect the second intermediate shaft 16 and the fourth
speed drive gear 24a together or release the connection. Then, when the second change-speed
shifter 52A is engaged in a second speed connecting position, the second intermediate
shaft 16 and the second speed drive gear 22a are connected together to rotate together.
When the second change-speed shifter 52A is engaged in a sixth speed connecting position,
the second intermediate shaft 16 and the sixth speed drive gear 96a rotate together.
When the second change-speed shifter 52A is in a neutral position, the second intermediate
shaft 16 rotates relative to the second speed drive gear 22a and the sixth speed drive
gear 96a. Additionally, when the fourth change-speed shifter 52B is engaged in a fourth
speed connecting position, the second intermediate shaft 16 and the fourth drive gear
24a are connected together to rotate together. When the fourth change-speed shifter
52B is in a neutral position, the second intermediate shaft 16 rotates relative to
the fourth speed drive gear 24a.
[0102] A third common driven gear 96b is mounted integrally on a countershaft 14 between
a first common driven gear 23b and a second common driven gear 24b.
Here, the third common driven gear 96b meshes with the seventh speed drive gear 97a
which is provided on the main shaft 11 and makes up a seventh speed gear pair 97 together
with the seventh speed drive gear 97a and meshes with the sixth speed drive gear 96a
which is provided on the second intermediate shaft 16 and makes up a sixth speed gear
pair 96.
[0103] A sixth speed running can be attained by engaging a second clutch 42 with the second
change-speed shifter 52A engaged in the sixth speed connecting position. In addition,
a seventh speed running is attained by engaging a first clutch 41 with the first change-speed
shifter 51A engaged in the seventh speed connecting position. In either of the cases,
the running of the vehicle can be assisted by a motor 7 or a battery can be charged
by the motor 7.
[0104] In the vehicle driving system 1A that is configured as has been described heretofore,
the vehicle can run on a 7
th EV mode in addition to a 1
st EV mode, a 3
rd EV mode and a 5
th EV mode.
Specifically, the 7
th EV mode is attained by shifting the first change-speed shifter 51A out of the neutral
position and engaging it in the seventh speed connecting position.
[0105] When the motor 7 is driven (torque is applied thereto in a forward rotating direction)
in this state, a sun gear 32 of a planetary gear mechanism 30 which is connected to
a rotor 72 rotates in a forward rotating direction. As this occurs, since the first
and second clutches 41, 42 are disengaged, power transmitted to the sun gear 32 is
not transmitted to a crankshaft 6a of an engine 6 from the first main shaft 11, but
motor torque is transmitted to drive wheels DW, DW by way of the seventh gear pair
97.
[0106] When the vehicle is slowed down which is running on the 7
th EV mode, likewise the downshifting from the 5
th EV mode to the 3
rd EV mode, a braking force may be ensured by controlling wheel brakes B1 to B4 in a
cooperative fashion during downshifting from the 7
th EV mode to the 5
th EV mode.
[0107] Namely, regeneration is executed in the 7
th EV mode with an accelerator pedal, not shown, released or OFF. Then, when the vehicle
speed is reduced to a predetermined value, the regenerative torque of the motor 7
is gradually lost, and at the same time, the wheel brakes B1 to B4 of the brake system
100 are actuated in a cooperative fashion so as to increase gradually the braking
force to be produced thereby in order to maintain a predetermined braking force. Then,
in such a state that the regenerative torque is completely lost, the first change-speed
shifter 51A is returned from the seventh speed connecting position to the neutral
position, while the third change-speed shifter 51 B is shifted out of the neutral
position to be engaged in the fifth speed connecting position. Following this, the
regenerative torque of the motor 7 is increased gradually, and regeneration is executed
in the 5
th EV mode. At the same time, in order to maintain the predetermined braking force,
the wheel brakes B1 to B4 of the brake system 100 are controlled in the cooperative
fashion so as to reduce gradually the braking force produced thereby. After the regenerative
braking force of the motor 7 in the 5
th EV mode reaches a predetermined braking force, the braking force produced by the
wheel brakes B1 to B4 of the brake system 100 is cut off, and the regeneration continues
in the 5
th EV mode. When the vehicle speed is reduced further to the predetermined value, downshifting
is executed from the 5
th EV mode to the 3
rd EV mode.
[0108] Thus, as has been described heretofore, according to the vehicle driving system
1A of this embodiment, when the vehicle is slowed down which is running on the 7
th EV mode by selecting the seventh speed drive gear 97a, the wheel brakes B1 to B4
of the brake system 100 are actuated in the cooperative fashion so as to compensate
for the reduction in regenerative braking force by the motor 7 while downshifting
is executed from the seventh drive gear 97a to the fifth speed drive gear 25a by use
of the first change-speed shifter 51 A and the third change-speed shifter 51 B while
regeneration is executed in the motor 7, that is, while downshifting is executed from
the 7
th EV mode to the 5
th EV mode while regeneration is executed in the motor 7, thereby making it possible
to ensure the braking force during downshifting.
[0109] In addition, the wheel brakes B1 to B4 of the brake system 100 are operated in the
cooperative fashion so as to compensate for the reduction in regenerative braking
force by the motor 7 while downshifting is executed from the 5
th EV mode to the 3
rd EV mode while regeneration is executed in the motor 7 in association with a further
deceleration of the vehicle, thereby making it possible to ensure the braking force
during downshifting.
[0110] Consequently, energy which is conventionally discharged as thermal energy while the
braking force is generated by the wheel brakes can be made effective use of as regenerative
energy.
[0111] In addition, when the vehicle is slowed down which is running on the 7
th EV mode, the braking force may be ensured by use of engine braking during downshifting
from the 7
th EV mode to the 5
th EV mode.
[0112] Namely, regeneration is executed in the 7
th EV mode in such a state that the accelerator pedal, not shown, is released or OFF
during EV running on the 7
th EV mode. Then, when the vehicle speed is reduced to the predetermined value, the
first clutch 41 is engaged to start the engine 6 while the regeneration continues.
After the engine 6 is started, the first clutch 41 is disengaged, and at the same
time, the second change-speed shifter 52A is shifted out of the neutral position to
be engaged in the sixth speed connecting position. Then, the second clutch 42 is gradually
engaged so as to apply engine braking. Then, after the second clutch 42 is engaged
completely, the first change-speed shifter 51A is shifted back into the neutral position
from the seventh speed connecting position, and at the same time the third change-speed
shifter 51B is shifted out of the neutral position to be engaged in the fifth speed
connecting position to thereby execute downshifting. Following this, regeneration
is executed in the 5
th EV mode, and the second clutch 42, which is engaged, is disengaged gradually. Then,
after the second clutch 42 is disengaged completely, the engine 6 is stopped. When
the vehicle speed is reduced further down to the predetermined value, downshifting
is executed from the 5
th EV mode to the 3
rd EV mode.
[0113] Thus, as has been described heretofore, according to the vehicle driving system 1A
of the embodiment, when the vehicle is slowed down which is running on the 7
th EV mode by selecting the seventh speed drive gear 97a, the engine 6 is started, and
the second clutch 42 is engaged in such a state that the sixth speed drive gear 96a
is selected by the second change-speed shifter 52A while downshifting is executed
from the seventh speed drive gear 97a to the fifth speed drive gear 25a by use of
the first change-speed shifter 51 A and the third change-speed shifter 51 B while
regeneration is executed in the motor 7, that is, while downshifting is executed from
the 7
th EV mode to the 5
th EV mode while regeneration is executed in the motor 7, thereby making it possible
to ensure the braking force during downshifting by making use of engine braking effects.
[0114] In addition, the engine 6 is started, and the second clutch 42 is engaged in such
a state that the fourth speed drive gear 24a is selected by use of the fourth change-speed
shifter 52B while downshifting is executed from the 5
th EV mode to the 3
rd EV mode while regeneration is executed in the motor 7 in association with a further
deceleration of the vehicle, thereby making it possible to ensure the braking force
during downshifting.
[0115] Consequently, in the vehicle driving system 1A of this embodiment, too, energy which
is conventionally discharged as thermal energy while the braking force is generated
by the wheel brakes can be made effective use of as regenerative energy.
[0116] The invention is not limited to the embodiments that have been described heretofore
but can be modified or improved as required.
Description of Reference Numerals and Characters
[0118] 1, 1A driving system; 6 engine (internal combustion engine); 6a crankshaft (internal
combustion engine output shaft); 7 motor (electric motor); 9 drive shaft; 11 first
main shaft (first input shaft); 12 second main shaft; 13 connecting shaft; 14 countershaft
(output/input shaft); 15 first intermediate shaft; 16 second intermediate shaft (second
input shaft); 20, 20A transmission; 22 second speed gear pair; 22a second speed drive
gear; 23 third speed gear pair; 23 a third speed drive gear; 23b first common driven
gear; 24 fourth speed gear pair; 24a fourth speed drive gear; 24b second common driven
gear; 25 fifth speed gear pair; 25a fifth speed drive gear; 26a final gear; 27A first
idler gear train; 27B second idler gear train; 27a idler drive gear; 27b first idler
driven gear; 27c second idler driven gear; 27d third idler driven gear; 30 planetary
gear mechanism; 32 sun gear (first element); 35 ring gear (third element); 36 carrier
(second element); 41 first clutch (first engaging and disengaging unit); 42 second
clutch (second engaging and disengaging unit); 51, 51A first change-speed shifter
(first changeover unit); 51B third change-speed shifter (first changeover unit); 52,
52A second change-speed shifter (second changeover unit); 52B fourth change-speed
shifter (second changeover unit); 53 reverse shifter; 61 lock mechanism (first changeover
unit); 96 sixth speed gear pair; 96a sixth speed drive gear; 96b third common driven
gear; 97 seventh speed gear pair; 97a seventh speed drive gear; 100 brake system;
111 brake pedal; B1 to B4 wheel brake; M master cylinder.